Single spindle automatic lathe



Get. 5, 1954 H. H. RANNEY 2,690,691

SINGLE SPINDLE AUTOMATIC LATHE Filed Sept. 15. 1949 ll Sheets-Sheet 1 11 Sheets-Sheet 2 277% Jriariljwzzy H H RANNEY SINGLE SPINDLE AUTOMATIC LATHE Get. 5, 1954 Filed Sept. 15, 1949 Oct. 5, 1954 RANNEY 2,690,691

SINGLE SPINDLE AUTOMATIC LATHE Filed Sept. 15, 1949 ll Sheets-Sheet 4 Oct. 5, 1954 H. H. RANNEY SINGLE SPINDLE AUTOMATIC LATHE l1 Sheets-Sheet 5 Filed Sept. 15, 1949 Oct. 5, 1954 H. H. RANNEY SINGLE SPINDLE AUTOMATIC LATHE 11 Sheets-Sheet 6 Filed Sept. 15. 1949 J/WW' kIZa/ZZIWWZ Oct. 5, 1954 H. H. RANNEY SINGLE SPINDLE AUTOMATIC LATHE ll Sheets-Sheet 7 Filed Sept. 15. 1949 wll miiiL Oct. 5, 1954 H. H. RANNEY SINGLE SPINDLE AUTOMATIC LATHE 11 Sheets-Sheet 8 Filed Sept. 15, 1949 @mww' ct. 5, 1954 H. H. RANNEY 2,690,691

SINGLE SPINDLE AUTOMATIC LATHE Filed Sept. 15, 1949 ll Sheets-Sheet 9 ct. 5, 1954 RANNEY 2,690,691

SINGLE SPINDLE AUTOMATIC LATHE Filed Sept. 15, 1949 ll Sheets-Sheet l0 Get. 5, 1954 H. H. RANNEY SINGLE SPINDLE AUTOMATIC LATHE l1 Sheets-Sheet 11 Filed Sept. 15. 1949 Patented Oct. 5, 1954 UNETEE ld l liltd httt ttl FHQE SINGLE SPINDLE AUTOMATIC LATHE Application September 15, 1949, Serial No. 115,804

'7 Claim". 1

This invention relates to automatic lathes, and more particularly to such lathes each of which has a single hollow work spindle through which lengths of stock are fed, tools being positioned for operation on portions of the stock which project beyond the spindle.

One object of the invention is to provide tool slides for supporting tools for operating upon the stock and which tool slides are fed into the work by power, as under fluid pressure, the rate of feed being positively controlled mechanically.

A. further object is to provide an improved end tool mechanism by which adjustment for straight or taper turning, or both, is made simple accurate.

Still another object is to improve the stock stop mechanism by which accurate setting for stock length for each work piece is facilitated.

Still another object is to provide improved means for supplying and feeding stock to the spindle.

A further object is to provide for automatic stopping of the machine when the stock supply becomes exhausted.

Further objects and advantages will appear from a description of an embodiment of the invention shown in the accompanying drawings in which Figures 1, 2 and 3 are front, right hand and left hand end elevaticnal views of a machine embodying the invention.

gure la is a fragmentary side elevation to ger scale of parts shown in Figure l. gure 4 is a rear elevation of the same.

Fi ure 5 is a diagrammatic View of a tool feed which results in breaking of the chips.

l igure '7 is a detail sectional view on line 'll of Figure 6.

sures 8 and 9 are detail sectional views on a view similar to Figure 13 but in different positions of adjust- Figure 16 is a detail sectional view on line it-it of Figure 11.

Figure 17 is a detail sectional view on line il-ll of Figure 16.

Figure 18 is a detail sectional view on line lt-ii of Figure 17.

Figure 19 is a development of the work spindle driving mechanism.

Figure 20 is a detail sectional view to a larger scale on line 2B2il of Figure 3.

Figures 21 and 22 are detail sectional views on lines ill-2i and 22-22, respectively, of Figure 1.

Figure 23 is a detail sectional view on line I 2323 of Figure 21.

Figure 2% is a wiring diagram showing the electrical controls for the machine.

Figure 25 is a diagram showing the hydraulic system of the machine.

Referring first to Figures 1 to 4, at i is indicated a machine base having at its rear end an upwardly extending column 2 within which is journaled a hollow work spindle 4. This work spindle is provided with a work clamp such as the collet shown enerally at 5 on Figure 2 at its forward end from which stock may extend, the extended portion being subjected to machining operations. The stock clamp 5 may be actuated by any suitable means but as herein shown it is actuated by axial motion of a spool 6 thereon which may pass more or less between clampactuating fingers l pivoted at 8 on a collar 9. Detailed showing of this stock clamp is not made herein since it is old and well known in the art and any desired clamping means such as is well known in the art may be employed.

The work spindle i is rotated, and for this purpose it is shown as provided with a gear it with which meshes a gear ll carried by a jack shaft 5 Fixed to rotate with the gear H is a long gear it with which meshes a gear I l splined to a shaft This gear I l is movable axially of its shaft while holding in mesh with the long gear it, so that this gear it may mesh with a relatively small drive gear it or a smaller gear 56 axially movable therewith may mesh with a or still smaller gear 98 may mesh with a gear is, the gears it, ill and i9 being carried on a drive shaft it. The gears i i, if; and is are carried by a quill 2i slidable on the shaft its such sliding may be accomplished by the rotation of a shaft 522 (see Figure 20) which has a pinion 2S thereon meshing with a rack portion of a bar B l. The bar 23 carries a yoke 25 which engages in a peripheral groove 26 in the quill 3 2!. The shaft 22 extends out through the casing of the machine and is provided with a handle 2! by which it may be turned, thus to determine which of the three sets of gears will be operative to drive the spindle from the drive shaft 20. The handle 21 may be latched in any of the three selected positions. The drive shaft also extends outwardly from the machine casing and has a splined portion for the reception of a belt pulley 3! over which may pass a V belt which passes about a drive pulley 32 on the main driving motor M.

The shaft 26 has journaled thereon a bevel gear 35 which may be clutched thereto by the closing of a clutch at 36 which may be accomplished by the axial motion of a clutch collar 31 shifted by a yoke 38 engaging this collar and being carried by a sleeve 39 guided for sliding motion on a stationary guide bar ii A link 4! connected to the slide 38 at one end is pivoted at 42 to a crank arm 43. The yoke is carried by an actuating shaft 44 which extends outwardly of the machine frame and carries an actuating handle 45 on one of its outer ends (see Figure 4) and with a second actuating handle it on the opposite face of the machine from the handle 65. It also carries an arm l! having a follower roll 48 actuated by cams (not shown) on a cam drum 49 on a horizontal cam shaft 58.

The spool 6 which is moved axially to clamp or release the stock may be moved axially by the swinging of a lever 59 (see Figure l) fingers 53 at its lower end engaging in the groove 54 of the clamp-controlling spool. The upper end of the lever is provided with a follower 55, positioned to be moved at suitable times by cams (not shown) on a drum 5? carried by the cam shaft. This cam shaft 58 is arranged substantially parallel to the spindle 4 and is positioned above this spindle.

The shaft 58 is driven at high and low speeds by a cross worm shaft 68 as shown best in Figure 8, this shaft 66 having a worm 6i thereon which meshes with a worm wheel 82 fixed to the cam shaft 58. It receives its fast driving motion from the bevel gear 35 on the shaft 20 which meshes with a similar bevel gear 63 carried by this worm shaft. In opposed relation to the bevel gear 63 is a second similar gear 64 carried on a short shaft 65 provided at its outer end with a suitable brake indicated at E55. This brake may be an electrically operated brake which is energized for a short period whenever the high speed clutch 36 is opened to slow the speed of rotation of the worm shaft to its low speed drive. Whenever the clutch 35 is closed the worm shaft 60 is in high speed drive position which is during the time that the work is not being machined, and when further operations, such as stock feeding and movement of the tool slides in retraction, or in moving up toward the work to the start of slow feed position, are taking place.

The slow feed drive, which is in force while the tooling operations are being performed on the work, is derived from the work spindle through mechanism at the opposite end of the shaft 68 as will later appear.

Side working tools As shown herein, three tool carriers Ni, ii and T2 (see Figure 16) have been provided, these being arranged at different angular positions around the axis of the spindle. Each of these tool carriers, as shown best in Figures 17 and 18, comprises a slide 15 mounted in a guideway It in the machine bed and retained in position in the guideway as by retaining plates 1'! which may be secured in position as by screws '58. Each of these slides '15 is provided with a cylindrical chamber for the reception of a fluid pressure cylinder 88 (see Figure 18) within which is slidably mounted a piston 85 carried by a piston rod 82. This piston rod extends through a cylinder head 34 provided with a suitable packing gland 85, and the outer end of the piston rod is secured in a bracket 86 secured to the machine frame as by screws 8?. The piston and piston rod are held stationary by the bracket 86, but the cylinder 80 being carried by the tool carrier slide is movable therewith. The piston rod 82 has a pair of fluid pressure passages 88 and 89 therethrough, the passage 88 opening out within the cylinder til on the piston head side through the port 99, while the passage 89 opens into the cylinder 88 at the opposite face of the piston as at 9!. Within a head 92 of the bracket 86 and in communication with the passages 38 and 89 are fluid pressure pipes through which fluid under pressure may be delivered to or discharged from opposite ends of the cylinder thus to drive the tool carrier toward or away from the Work spindle.

Each of the slides carries a short shaft I 33 on which is journaled a cam follower roll it! and each of these cam follower rolls is adapted to be moved into or out of engagement with a corresponding cam I62 adjus'tably carried on cam ring H35 journaled on a pair of supporting rings H39 carried by the spindle 4 and suitably clamped thereon. Tre cam ring I has attached thereto, as by screws H0, a worm gear ring H:

with which meshes the worm M of the cross shaft 68, so that the cam ring W5 is rotated thereby concentric with the wort: spindle but at a slower rate, this rate being detern ined by the rate of rotation of the worm shaft 62. These parts are so arranged and their motions are so timed that the tool carrier slides are moved inwar ly when the high portions of the cams 582 are in position to be contacted by the follower rolls 581, and during the slower working speed rotation of the shaft 68 the engagement Of the cam followers [ti on the cams I02 and the movement of these cams :02 in clockwise direction, as viewed in Figure 16, determine the rate at which the carriers approach the work. Thus the feed of the tools relative to the work during their operative or cutting action is effected by power produced by the fluid pressure mechanism, but the rate of such feed is controlled mechanically by the cams I82 and their slopes and rates of motion.

Slow feed The slow feed rotation of the shaft 59, as before noted, is produced by driving mechanism at the opposite end from the high speed drive derived from the shaft 29, and as .iown herein this slow speed drive is accomplished at a variable rate so that the chips cut by the tools are of irregular thickness which results in breakage of the chips so that they do not come off in long continuous lengths which are troublesome to handle in the machine.

The mechanism for producing the slow rotation of the worm shaft 63 is shown best in Figures 6, 7, 9 and 10 and its drive mechanism is shown best in Figures 9 and 19. Referring to Figure 19, the spindle l is provided with a helical gear i211 with which meshes a similar gear I25 (see Figure 9) carried by a shaft i 22. This shaft I22 extends into a casing I23 normally closed by a cover plate I24. Within this casing I23 there is fixed to the shaft I22 a disk I25 having a slideway I 26 arranged diametrically thereacross (see also Figure 6). Within this slideway is mounted a block I21 which is adjustable toward and from the axial center of the disk by the turning of a threaded shaft I28 journaled at I29 in a rim portion I30 of the disk I25. This slide I21 has a journal member I3I extending therefrom which can be adjusted by adjusting this block so that it is eccentric to the axis of the shaft I22 to any desired extent. Journaled on this journal member I3! is a second block I slidable between parallel guides I36 in a bell crank lever I31 which is fulcrumed at 33 on a fixed pivot. As the shaft I22 rotates, therefore, the rocking motion is produced by the bell crank lever I31, the amplitude of which is dependent upon the amount of eccentricity of the journal I3I with respect to the shaft I22. motion is made to produce a periodic turning of the worm shaft 60 whenever this worm shaft is not driven at its fast speed through the fast speed drive mechanism hereinbefore described The opposite arm M0 of the bell crank lever I31 is forked, one branch having fixed thereto, as by screws I lI, an arcuate segment I d2 of an in ternal gear, and the other branch of the fork I43 carrying a segment lid of an external gear. The segment I l-2 meshes with a segment I 25 of an external gear projecting outwardly from a ring I 36 (see Figure '7) which is journaled on a hub portion I41 (see Figure 10) with the outer face of which it is connected by a one-direction clutch mechanism comprising three rollers I lt seated in tapering depressions M9 in the hub It? and urged into clutching engagement by springs I50. This arrangement is such, as may be seen by an inspection of Figure 10, that when the ring I 45 is rotated in clockwise direction it is clutched to the hub M1 which is thus rotated in the same direction, but during the reverse direction of turning of the ring I4 5 it is freed from clutching engagement with the hub i l"! which does not turn in this direction therewith.

The segment I64 which meshes with a segmental portion I of a sleeve I55 is effective upon the rocking of the shaft i22 to turn this sleeve I56 through a small angle in opposite directions. When the sleeve I56 is turned in a clockwise direction, it is clutched by the roller clutch elements I51 to the inside face of the hub portion I 41, while when it is rocked counterclockwise it is unclutched therefrom. Bushings E62 may be interposed between the ring 369 and the hub portion I41 and between the hub portion I s1 and the sleeve E55. Thus the hub portion M1 is rotated step by step in clockwise direction, as viewed in Figure 10, and it has a ring portion I adapted to be clutched to the worm shaft 63 by the closing of the clutch IEI.

The clutch IBI is actuated by the shifting of a member I63 having a yoke I65 engaging in a groove I65 in the clutch spool I56. The member I63 is carried by an axially movable rod I61 provided with a rack portion engaged by a gear segment I63. The gear segment :63 forms a portion of a lever I69 which is connected through a link I1Il with an arm I1I (see Figure 8) carried by a rock shaft I12. This rock shaft extends out through the machine casing where it is provided with a handle I13. The shaft I12 which carries the arm I1I is also provided with an actuating handle I14. During normal operation the low speed This rocking clutch I6I remains closed. When the high speed clutch is closed, the low speed clutch, including the two one-way roller clutches previously described, acts as an overrunning clutch which allows the high speed drive to take over the control and drive the worm shaft 8!}. When the high speed clutch is open, the drive is taken over by the low speed clutch. When setting up, however, it is often desirable to open the low speed clutch IBI.

The efiect of the intermittent drive of the low speed clutch on the chip produced by a turning tool is illustrated in Figure 5. The turning tool A is caused to be fed at varying rates as the cam ring I is driven at a variable rate of speed and with a controlling cam Hi2 having a gradual iminterrupted slope. The effect, as shown in Figure 5, is to produce a chip having alternate relatively thin portions as at x and relatively thick portions as shown at y, with intermediate portions of intermediate thickness. This results in the chip being of vardying strength, the chip breaking at the thinner portions and thus coming off from the work in disconnected short lengths. The particular mechanism by which this chip breaking is effected is not a portion of the present invention but forms subject matter of an application for patent of Roger W. Brown, Serial No. 118,083, filed September 27, 1949.

The final limits of feed are determined by positive stops 583 on the tool slides striking fixed frame portions and independent of the cams I02, so that true final diameters are assured.

End working tools and mounting Extending parallel to the axis of the work spindle and forwardly from the column 2 are a pair of spaced guide bars 20%] which are supported at their outer ends in a downwardly extending bracket 29! carried by an upper frame member 2212 which extends forwardly beyond the forward end of the work spindle. The rear ends of the bars extend into the column 2 where they are rigidly supported. Slidably carried by these bars is a main tool slide 293. In its upper portion the slide 223 is provided with a cylindrical chamber 2% within which is positioned a hydraulic cylinder 2&5. This cylinder contains a piston shown in dotted lines in Figure 11 and its piston rod 291 extends out through a suitable head which may be similar to that shown in Figure 18 for the side working tools, and is fixed in the top frame member 2&2. The piston rod contains suitable fluid pressure passages simil to that shown in Figure 18 whereby pressure may be introduced into the pressure chamber on either selected side of the piston 2% thereby to move the main tool slide 293 lengthwise of the guide bars and thus in predetermined angular relation to as shown, in parallel relation to the work spindle. The lower face of the tool slide is provided with T-slots 21s to facilitate attachment thereto of a suitable tool holder. The tools carried by this holder are thus given a motion parallel to the work axis as the main tool slide 2% is moved along the guide bars This main tool carries a secondary tool slide 2N5. This slid-e 25d, as shown best in Figures 12, 13 and 14:, is formed with T slots for the attachment of tool holders similar to the T slots i it of the slide arranged to slide up down across the vertical face 2 i 5 of the main tool slide 283 and it is held thereagainst as by a dial member Zlii which bears against the outer 7 face of the secondary tool slide as shown in Figure 12. It is slidably guided for motion transverse to the bars 200 as between the side guide members 2|! shown best in Figure 1. The face portion N5 of the main tool slide is formed with a longitudinal way 2m therein within which is slidably guided a bar 229 (see particularly Figures 11, 12, 13 and 14). This bar 2% has journaled therein a pivot portion EZl of a block 222. The block 222 has parallel side portions 223 and 224 which are slidably guided in a diametrical slot 225 in a disk 226 which is journaled in a circular recess in the inner face of the secondary slide 2M (see particularly Figure 12). This disk 22B is provided with a coaxial pivot portion 22'! which has a Worm gear portion 223 thereon with which meshes a worm 229 on a Worm shaft 230 having an adjusting knob Z3l on its outer end. A set screw 233 passes through the dial member 2H3 and threads into the outer end of the pivot portion 221 to lock it against accidental turning. The bar 220 has attached thereto the inner end of a rod 2&9 threaded for the major portion of its length and extending through a hole in the bracket 29!, outwardly of which it has threaded thereon a pair of check nuts 242. Between the bracket 29! and the end of the bar 223 there is a similar pair of check nuts 2 2-3 threaded thereon. These pairs of check nuts act as stops to limit the sliding motion of the rod 24-8 through the bracket 20 l. Thus as the main tool slide is moved inwardly, carrying the secondary tool slide with it, the bar 220 is moved with both until the check nuts 242 impinge on the outer face of the bracket 2!. Further motion of the bar 220 with the main and secondary tool slides is then stopped and such motion causes sliding of the block 222 within the guideway 224. If this guidaway is positioned parallel to the motion of the main tool slide in the position shown in Figure 13, the secondary tool slide continues on its parallel motion, but should the guide 224 be turned at an angle to the direction of motion of the main tool slide, the secondary tool slide is given a motion transverse thereto, depending upon the extent of such angular adjustment. Such position is shown, for example, in Figure 14 wherein the secondary tool slide, after the motion of the bar 220 has been stopped, is given a downward motion as far as is permitted by the block 222 engaging the Wall of the journal opening 22 5. This results in the secondary tool slide being given a motion, which, when imparted to a tool carried thereby, produces a taper cut on the work depending in amount of the taper on the angular adjustment of the disk 228. Return motion of the main slide moves the secondary slide with it until the motion of the bar 223 is stopped by the check nuts 243 striking the bracket 20!, whereupon further motion of the main slide returns the secondary slide to starting vertical position. It is thus possible with this mechanism to out either straight or taper, and if desired, both at the same time. For example, the outside diameter of a tubular work piece may be cut straight and the inside diameter tapered.

In order to provide against any lost motion in these parts, the secondary tool slide is pulled upwardly sufficiently to take up such lost motion, as by a pair of springs 235 surrounding posts 236 secured at their lower ends in the secondary tool slide, and projecting through openings 23"! in a top cover plate 238 extending across the top face of the main tool slide. These springs 235 bear between Washers engaging the top face of the plate 238 and washers held by check nuts 239 threaded on the upper ends of the rods 236.

It will be noted that the secondary tool slide par-takes of the parallel motion of the main tool slide during the high speed movement of the tool slides required to bring the tools up close to the work and during final retraction, but that when the tools are actually operating upon the work, the bar 220 may have reached its limit of motion with the main tool slide so that during the cutting action of the tool or tools carried by the secondary tool slide the angular adjustment of the disk 226 controls the extent of taper.

Stock feeding and control mechanism Positioned at the back part of the machine are a pair of spaced stands 300 and 381, which are connected at their upper ends by a pair of spaced guide bars 302 and above them a pair of downwardly and inwardly inclined trough members 303. These trough members are so positioned as to support a piece of stock 334 in substantially axial alignment with the hollow of the work spindle. Slidably guided on the guide bars 392 is a feed carriage 305 supporting a feed rod 366. This rod 393 at its inner end supports a rotating plunger head 3680 and may engage in a split bearing 3M in the carriage 385 which may be clamped into engagement with the bar 306 by tightening a screw 308. The plunger head 3666 may engage the rear end of the piece of stock 30 3 and by moving the head 3050 forward- 1y, or to the right, as shown in Figures 1 and 23, the piece of stock may be fed into the spindle and through it at suitable times as far as permitted by a stock stop which will later be more fully described.

The feeding and retracting motions of the plunger 3966 may be produced by suitable driving mechanism, herein shown as comprising an endless chain 386i secured at 399 to the feed carriage 395 and arranged to pass around end sprocket wheels am and 3! The sprocket wheel Sin is journaled on the inner stand 39! and the outer sprocket wheel 3 i l is journaled on the rear end of a bracket arm 3l2 extending rearwardly from the stand 360. From the sprocket wheel 3 the chain 306] travels downwardly and forwardly around a driving sprocket wheel 3 Hi, then upwardly around a guide and tensioning sprocket wheel 3l5 journaled on a spring pressed arm 3!! pivoted on the bracket arm 312, and then substantially horizontally to the sprocket wheel am. The driving sprocket 3 I4 is carried by a shaft 3H3 which is connected through a reduction gearing and slip clutch shown generally at 320 to a reversible motor SM. By reversing this motor at suitable times, the direction of travel of the stock pusher plunger 3666 may be changed, thus to cause a piece of stock to be fed into the spindle from time to time as desired, the feeding carriage being then retracted to permit a new piece of stock to come into place forwardly of the plunger 3060 so that this stock piece may be thereafter fed into position.

Stock may be supplied to a position in front of the stock feed carriage and may be arranged on an inclined bed 336 as shown in Figure 22, this inclined bed sloping downwardly to the trough formed by the members 303. lhe pieces of stock may be allowed to descend one at a time into feeding position by means shown in Figure 22, which comprise a pair of stop posts 33! and 332 having shoulder portions 333 for engagement with the stock. As shown these posts are mounted for vertical sliding movement in a pair of ways (itl and 335 and their confronting faces may be formed of rack portions 355 and 337 which mesh with a gear 338 carried by a rock shaft 339 positioned between the stop posts. By rocking the shaft 33% one or the other of these posts may be projected above the top face of the membr 335 while the other is being lowered therebeneath. Thus in the position shown in Figure 22, by lowering the left hand post 53!, the work piece 3540, will be released so that it may roll down into the feeding trough, while the post 332 will be projected up into the path of motion of the work piece 384?) next above, which will prevent this work piece and any above it from descending further toward feeding position. On reverse rock ing of the shaft 339, the left hand post will be lifted and the right hand post 332 depressed, allowing the work piece 354?) to pass down until stopped by the post 33f in the position occupied in Figure 22 by the work piece 585a. An arm 3 35 adjustably carried on a post 3 32 projecting up wardly from the adjacent standard acts to retain the work pieces against the top face of the bed 53ft so that they cannot pass the post 335 when it is in elevated position,

The shaft 335 extends from the standard 351 through the standard 355 and out toward the outer end of the bracket 3 l 2 and is provided at its ends with spiral gears 355 with which mesh spiral gears 345 on a pair of rock shafts 3M. These rock shafts are provided with fingers 348 in position to be engaged by the work piece and by the carriage 355 when it approaches the limits of its motions. As the feed carriage 305 approaches its outer limit of motion, the shaft Zit'l is rocked to the position shown in Figure 23, which acts to rotate the gear 338 in direction to permit the foremost piece of stock on the supply member 339 to be released so that it rolls into position to be engaged and fed forwardly by the feed plunger 39%. When the bar of stock strikes the inner finger 348 of the inner shaft 34?, the gear 333 is rocked in the reverse direction, returning the stop fingers 33! and 332 to the position shown in Figure 22, allowing the next succeeding piece of stock to move into position for release to feeding position when the stock feeding means has next been returned to fully retracted position. A switch LS9 at the entrance end of the spindle and carried by the stand 36! is in position to be engaged by a pin 35! projecting from the feed carriage 335 which acts to deenergize the main motor M to stop the machine as will later more fully appear.

Stock stop Rockably carried on the forward face of the column 2 is an arm 315 carrying a stock stop 3'55 at its outer end. This stop is adapted to be adjusted on the arm 3l5 from and toward the forward face of the column and when the arm 375 is in its inoperative position shown in Figure 1 and in full lines in Figure 25, it is positioned opposite to a fixed abutment til. This abutment is arranged accurately in line with the rear edge of the cut-off tool carried by one of the side tool carriers, and herein shown as the central carrier 7i, so that when the stock stop 315 is adjusted at a predetermined accurate distance therefrom, as by means of measuring blocks placed therebetween, itwill be correctly positioned to measure off the desired length of stock projecting from the work spindle when it is turned into its upper position shown in dotted lines in Figure 25 with its stop portion 376 in line with the work spindle. When the work is to be fed, therefore, the stock stop is arranged to be swung upwardly into operative position and the stock is fed until it strikes against the stop, after which the stock is clamped in the spindle and the stop is returned to its inoperative lowered position.

As shown in Figure 25 the movement of the stock stop is actauted hydraulically by a motor of the vane type shown at 385 having a gear 33! on its actuating shaft meshing with a pinion 352 on the pivot shaft 383 of the arm 375.

Contnolling mechanism and cycle of operation The machine controlling mechanism comprises the hydraulic system contained in a unit lflii which may be placed in a recess llll in the base of the machine. This unit, as shown in the diagram of Figure 25, comprises a supply tank 482, and a high pressure low volume pump 483 driven by the motor HM which delivers liquid under pressure from the tank through the sequence valve iii l into the pressure line 595. Excess fluid from the line 505 is discharged through the line 4334 into the line 656. A low pressure large volume pump 3235 driven by the same motor PM also delivers liquid from the tank 452 past a check valve dill into the pressure line 558. The pressure line 685 also communicates through a pressure relief valve @539 with a discharge pipe 459. Fluid under pressure from the line 458 and discharge to the pipe MB for the several hydraulically actuated tool slides Iii, H, 72 and 25 i and to the stock stop vane motor 339 are controlled by four-way valves actuated by electrically moved rack bars and pinions as will later more fully appear.

Simplified electrical controls for the machine are shown in Figure 24 in which the main motor M, the hydraulic pump driving motor HM, and the stock feed driving motor SM are shown as energized from the three-phase power lines 500, 506 and 552. Across the lines 500 and 562 is the primary 5% of a transformer, the secondary 505 of which provides low voltage current for the control circuits. A push button panel 499 is located on each of the front and back faces of the machine as shown in Figures 1 and 4, each panel including a start button 510 and a stop button 5| i. Jog switch buttons may also be included, but the circuits therefor and various safety circuits which may be used are not shown on Figure 24 as they do not form part of the present invention and to avoid further complicating the diagram of Figure 24. Each start button 5 i 5 when depressed closes a circuit for the transformer secondary 505 through leads 5135, 55?, the start button 510, the closed stop buttons 5i i, lead 5 l 2, closed switch 5 I3 of relay CRS, lead 5M, solenoid 5| 5 of the main motor switch 555, leads 5H, 5|8 and 5I9, back to the lead 525 from the transformer secondary 505. Energization of the solenoid 515 closes the switch which energizesthe main motor M from the three phases; from line 586 through loads 52!, 522, closed switch 523, and lead 524 to the motor M; from line 56! through lead 525, closed switch 526 and lead 527 to the motor M; and from line 552 through leads 55 i, 528, switch 529 and lead 530 to the motor M.

The hydraulic motor HM is started by closing the manual switch 535, which establishes a circuit from the lead 555 through leads 536, closed switch 535, lead 531, solenoid 538 of the hydraulic motor EM switch 535, lead 540 to the return lead 520. This switch 539 remains closed during the ll entire operation of the machine. Closing of the switch 539 connects all three phases of the power line to the hydraulic pump motor, from line 555 through leads 52!, 555, closed switch arm 545 of the switch 539, and lead 557 to the motor HM; from line 50! through lead 558, closed switch arm 549 of the switch 539 and lead 555 to the motor HM; and from line 552 through leads and 551, closed switch arm 552 of the switch 539 and lead 555 to the motor HM.

t the start of the cycle all of the tool carriers are retracted, and the switches LS5, LS5, LS and LS! are each open. The switch 555 is closed by the operator, this energizing the solenoid of relay CR5 from the lead 555 through the leads 557 and 55!, closed switch 558 and lead 552 to the solenoid of relay CR5 to leads 553 and 5E9 back to lead 520. Energizing of the relay CR5 closes its switch 565 which, however, does nothing until such time as the machine cam shaft reaches the angular position to close a switch LS1, which is when the low speed rotation of the cam shaft starts and which is actuated by a suitable cam dog carried by this shaft. Switches LS2 to LS? and switch LSifi are also actuated by dogs carried by cam shaft 58 at suitable angular positions as shown in Figure 1a. Closing of both switches 564 and LSI closes a circuit through solenoid 555 of the hydraulic valve 557 of Figure 25, which places this valve in the condition shown in Figure with the inner end of the cylinder '52 in communication with the pipe 558 with a pressure pipe 458, while the rear end of the cylinder 72 is open to the discharge pipe 415 through the pipe 569 and the valve 55?. The hydraulic valve 55'! remains in this condition even though switch LSi opens. The solenoid 555 which moves the valve to this position is energized from the lead 555 through leads 595, closed switch 555 of the relay CR5, lead 59!, closed switch LSl, lead 592, solenoid 556, and leads 593, 585, 585 and 5'58 to the lead 52 5. The rear tool slide is thus moved inwardly until its cam roller 55! strikes the corresponding cam I52. Since there is little resistance to this motion of the tool slide, it is moved rapidly by the action of the high volume low pressure pump 555, but when its rapid motion is stopped, the pressure is increased by the action of the high pressure pump 453 which acts through the sequence valves Q34 and 512 to increase the pressure with which the tool slide is moved inwardly. A check valve 5' prevents any reverse flow from the cylinder 72 and a sequence valve 512 admits fluid under high pressure when the rapid feed of the slide is stopped. The back tool slide '72 continues to move inwardly under high pressure and at the slow working speed controlled by the scope of its controlling cam Hi2 and the low speed rotation of the ring I55 which carries this cam. The limit of inward feed of this slide is determined by a positive stop I85 and when its roughing operation has been completed, the switch LS3 is closed by the cam shaft, the switch LSI now being open. Closing of the switch LS3 closes a circuit through the solenoid 515 of the relay CR3 from the lead 555 through the lead 516, closed switch LS8, lead 5', coil 575 of the relay CR3, and lead 578 back to the lead 525. Closing of the relay CR3 closes several switches including switch 5l9, which acts to return the tool slide 12 to retracted position. Closing of the switch 579 establishes a circuit from lead through the lead 585, closed switch 5'59 of the relay CR3, leads 581 and 582, retire solenoid 583 of the valve 567 and leads 584, 585, 585 and 578 to the lead 520. This reverses the hydraulic valve 557, connecting the pipe 559 to the pressure pipe 558 and connecting the pipe 558 to the discharge pipe 5E5. Since there is little resistance to the return motion of the slide, it returns at high speed produced by the action of the low pressure high volume pump 456.

The closing of both switches LS! and 554 also starts the feed motion of the finish tool slide 75, the end working tool slide 253 and the cutting on slide 7 l, but the cutting actions of each of the slides 70 and ll is controlled by the contour of its own cam 52, the finishing tool on the slide Ell following behind the roughing tool so that it does not come into action until the completion of the roughing cut. The closing of the switches LS! and 554 energizes the solenoids 650 and Bill of the finishing and end working tool slides, respectively, and 552 for the cut-off slide H. The solenoid 655 for the finishing tool slide is energized from the closed switch LS! through leads 592 and 6M, solenoid 605 and lead 505 to the lead 585. The solenoid 5!]! is energized from the switch LSI through leads 592, E56, solenoid Gill and lead 65? and 655 to the lead 585. The solenoid 552 for the cut-off slide is energized from the switch LS! through leads 552, 608, solenoid E52 and lead 615 to the lead 585. The solenoids 555, Bill, and 652, when energized, move their respective hydraulic valves (H5, SIG, GIT into the position shown in Figure 25, connecting the pipes 5l8, (H9 and 525 leading to the inner ends of their respective cylinders 70, 2G4 and H to the pressure pipe 458, and pipes 52!, 522 and 623,

1 respectively, leading to the opposite ends of the cylinders, to discharge. Sequence and check valves 62 i and 525 are arranged in these lines similar to the corresponding valves in the roughing tool control system previously described. The finished tool slide and the end working tool slide are returned by energization of hydraulic valve controlling solenoids B and 53l and are controlled by the return control for the roughing cut by the closing of the relay'CR3.

These controls are as follows. Closing of the relay CR3 closes a switch 635 which energizes the solenoid 635 from lead 505 through lead 536, closed switch 535 of relay CR3, lead 531, solenoid 535 and leads 539, 585, 585 and 518 to the lead 525. Closing of this relay CR3 also closes a switch 545 which energizes solenoid 63! from the lead 556 through leads 641, closed switch 550 of the relay CR3, lead 542, solenoid 53! and leads 639, 585, 585 and 578 to lead 520.

The cut-oif tool slide H is returned by the closing of the switch LS2 which is actuated by a suitable dog on the cam shaft 58. Closing of this switch LS2 energizes the solenoid 55B of the cut-off tool slidecontrol valve which reverses the valve Gil, connecting the pipe 523 to pressure and the pipe 525 to discharge. Closing of the switch LS2 energizes the coil 55I of the relay CR2 from the lead 555 through closed switch LS2, lead 552, coil 55! of the relay CR2 and lead 553 to the lead 520. Closing of the relay CR2 closes a switch 654 which energizes the reverse hydraulic solenoid 559. This circuit is from the leads 505 through lead 655, closed switch 554 of the relay CR2, lead 657, solenoid 650 and leads G59, BIO, 585 and 5218 back to the lead 520.

After the tools have done their work and have retracted, the cam shaft reaches an angular position at which cams (not shown) on the drum [8| close the high speed clutch 35 so that the cam shaftis now driven at its high speed from the 13 shaft 2d, and when this has been accomplished, the chuck is opened mechanically by cams on the cam drum which swings the lever 59 in counterclockwise direction as viewed in Figure 1. The stock stop Bit is then swung up into operative position by the closing of a switch LS!!! which is positioned adjacent to the cam shaft and is actuated by a suitable dog thereon, as previously described. Closing of this switch LSlll energizes the stop lifting solenoid 663 (Figures 24 and 25) by closing a circuit from the lead 5% through the lead 65!, closed switch LSIQ, solenoid 686, and lead 862 back to the lead 52d. The switch LSlil is held closed until after the feed of the stock has occurred, and it is then allowed to open so that the stock stop may be returned to inoperative lowered position shown in Figure 1. A spring 656 engaging the rack bar 5% returns the valve 583 to its inoperative position shown in Figure 25.

Stock feed The stock feed is produced by forward motion of the stool: feed motor SM which is effected by the operator, who closes the manual switch FOR. This closes a circuit from lead 585 through lead closed switch FOR, lead 68?, closed switch 3t closed manual reverse time delay switch 669, lead EEJ'il, solenoid of relay CRT and lead 557! back to the lead 5:219. Closing of the relay CR'l closes a switch hi2 which closes the controlling switch to the stock feed motor SM from the lead 506 through leads tic, closed switch 672 of the relay CRl, lead sit, closed switch 619 of relay CR6, lead closed switch 65H of relay CR4, lead to the coil 633 of the forward switch F of stock feed motor, leads '88s, tit, and 5H) to the lead 525?. The feed motor SM continues to work until the stock strikes the stock stop, whereupon the slip clutch in the unit 32B in the motor drive slips until the chuck opens and the stock is again fed forward to the stock stop and so repeats. Meanwhile the switch LS3 has been closed by a dog on the cam shaft 58 which conditions the circuit by energizing the coil 575 of the relay CR3 which closes the switch 69! and opens the switch Still so that when a limit switch LS9 is contacted by the feed carriage when the feed has progressed to its forward limit, the machine will be stopped, and the stock feed motor SM reversed to retract the feed carriage automatically, and after a predetermined time the motor SM is stopped by the time delay switch 669. This action acts as a signal to the operator and allows the operator to remove short ends of stock from the spindle, and re-stock the carriage with new bars after which he may start the machine again by pressing either of the start buttons. Pressing a forward feed button starts the motor SM and causes a new bar of stock to contact any remaining stock left in the spindle, pushing it against the stock stop, the slip clutch then again coming into action.

Reversing of the feed motor is effected as follows. The switches LS3 and LS9 being closed, a circuit is closed from the lead 566 through closed switch LS9, leads 698, closed switch 69! of the relay CR3, lead 392, coil of the relay CR5 and leads 5553 to the lead 529. Closing of the relay CR8 opens the switch 6'19 in the circuit which closed the forward feed motor switch, thus causing the forward switch F to open. Closing of the relay CR6 also closes a switch 695 which acts to throw in the reverse direction return switch R for the stock feed motor SM as follows. Circuit is made from the lead 506 through lead 615,

closed switch 612 of the relay CRY, leads 696 and 691, closed switch 695 of relay CR6, lead 698, coil 699 of the relay R, leads lilll, Elli and M9 to the lead 52!]. Closing of the relay R causes the feed motor to operate in the reverse direction, its switch reversing the connections of the motor to the lines 50! and 532. The automatic stopping of the machine motor M is effected as follows. When the switch LS3 at the drum shaft was closed, the relay CR3 was energized and the normally open switch LS9 was closed by the feed carriage, this, in turn, energizing the relay CR6. When the switch LS3 is allowed to open by its cam, it deenergizes the relay CR3 which closes a circuit from the lead tilt through the lead 726, normally closed forward contacts 666, through lead 625, closed switch 72:2 of the relay CR5, lead 692, closed switch lSQl, lead I26, switch 796 of relay CR3, lead 728, switch 188 of the relay CR2, to the coil 235 of relay CRS, through lead ml to lead 520. Energizing the coil of the relay CRS holds the switch M3 open, which closes down the main motor M.

Certain unnumbered switches and leads shown in the diagram are portions of so called safety circuits, but as they are not material to this invention, they are not described herein.

When during the cycle the cam shaft til opens the high speed clutch at 36, allowing the low speed drive to take over, the rotation of the worm shaft Ell is slowed to the rate of the low speed drive by the brake 5%, as heretofore described. This brake is electrically actuated by the energizing of the solenoid l i ii through a rectifier H6 across the time delay ill interposed in a circuit from the lead 55% through leads H8 and H9, and switch LS8 which is closed by lever I69 when it opens the clutch 3d. The brake remains on for a time, controlled by the setting ,of the time delay ill in each cycle of operation of the machine.

From the foregoing description of an embodiment of this invention, it will be evident to those skilled in the art that various changes and modifications may be made without departing from its spirit or scope.

I claim:

1. In combination with a rotary spindle, a work holder carried by said spindle, a cam ring journaled on said spindle, means for rotating said cam ring at a slower rate than said spindle, a tool carrier movable toward and from said spindle, a tool carried by said carrier for operation on work carried by said work holder, a follower on said carrier, a cam on said ring and against which said follower may ride, power means for pressing said carrier toward the work and with its follower riding on said cam and for retracting said carrier, and means controlling said power means.

2. In combination with a rotary spindle, a work holder carried by said spindle, a cam ring journaled on said spindle, means for rotating said cam ring at a slower rate than said spindle, a tool carrier movable toward and from said spindle, a tool carried by said carrier for operation on work carried by said work holder, a follower on said carrier, a cam on said ring and against which said follower may ride, fluid pressure means for pressing said carrier with its follower riding on said cam to press said tool against the work and for retracting said carrier, and means controlling said fluid pressure means to advance and retract said carrier and its tool with respect to the work.

3. In combination with a rotary spindle, a work holder carried by said spindle, a cam ring journaled on said spindle, means for rotating said cam ring at a slower rate than the rotation of said spindle, a plurality of tool carriers arranged angularly spaced around the axis of said spindle, each carrier being mounted for motion toward and from work carried by said work holder, a cam follower on each of said carriers, a cam for each of said followers carried by said ring, power means for pressing said carriers toward said work holder as far as permitted by said follower riding on said cams and for retracting said carriers, and means for controlling said. power means.

4', In combination with a rotary spindle, a work holder carried by said spindle, a cam ring journaled on said spindle, means for rotatin said cam ring at a slower rate than the rotation of said spindle, a plurality of tool carriers arranged angularly spaced around the axis of said spindle, each carrier being mounted for motion toward and from work carried by said work holder, a cam follower on each of said carriers, a cam for each of said followers carried by said ring, power means for pressing said carirers toward said work holder as far as permitted by said followers riding on said cams and for retracting said carriers, a rotary shaft, means for rotating said shaft in time with the rotation of said spinle, dogs carried by said shaft, and controlling means for each of said power means arranged in the path of motion of their respective dogs for actuation by said dogs in time with the angular positions of said shaft.

5. In combination, a hollow rotatable work spindle through which a work piece may extend, a tool holder having tools including a cut-off tool for operating on work projecting from one end. of said spindle, a machine bed carrying said spindle and supporting said tool holder, an abutment carried by said bed in definite relation to the inner edge of said cutting oif tool, and a stock stop carried by said bed and movable between a position in line with said spindle to limit the feed of stock through said spindle and a position opposite to said abutment, said stock stop having a stopping portion adjustable in a direction substantially parallel to the axis of said spindle, said abutment serving when said stop portion is opposite thereto as a reference from which measured adjustment of the spacing of said stopping element may be made to thereby determine the length of stock feed after cut-off has been effected.

6. In combination with a rotary work holding spindle, a tool carrier mounted for motion toward and from work held by said spindle, a cam mounted for motion concentric with said spindle, a follower for said cam carried by said tool carrier, power means for moving said carrier toward and from said spindle and said follower toward and from said cam, the engagement of said follower on said cam limiting the depth of cut of a tool on said carrier with respect to work held by said spindle, means for controlling said power means, means for rotating said spindle, and means for turning said cam at a different rate from said spindle while said follower is in engagement with said cam whereby the contour of said cam controls the rate of feed of said tool by said power means as said cam is turned.

7. In combination with a rotary work holding spindle, a tool carrier mounted for motion toward and. from work held by said spindle, a cam ring journaled coaxially with said spindle, a cam carried by said ring, a follower for said cam carried by said tool carrier, power means for moving said carrier toward and from said spindle and said follower toward and from said cam, the engagement of said follower on said cam limiting the depth of cut of a tool on said carrier with respect to work held by said spindle, means for controlling said power means, means for rotating said spindle, and means for turning said ring at a different rate from said spindle while said follower is in engagement with said cam whereby the contour of said cam controls the rate of feed of said tool by said. power means as said ring is turned.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 120,593 Miller Nov. 7, 1871 627,385 Brockie June 20, 1899 1,467,304 Bosshard Sept. 11, 1923 1,635,285 Lovely July 12, 1927 1,762,983 Hogg June 10, 1930 1,954,964 Tessky Apr. 17, 1934 1,956,999 Rupple May 1, 1934 2,029,638 Ruppel Feb. 9, 1936 2,092,202 Bennett Sept. 7, 1937 2,255,170 Kelley Sept. 9, 1941 2,257,729 Bosworth Oct. 7, 1941 2,369,466 Kylin et al Feb. 13, 1945 2,425,308 Drissner Aug. 12, 1947 2,441,533 Montgomery May 11, 1948 2,480,319 Brodhun Aug. 30, 1949 

